Turbine driven centrifugal machine



June 18, 1946. H'ERTR-ICH 2,402,496,

TURBINE DRIVEN GENTRIFUGAL MACHINE Filed June 18, 1941 5 Sheets-Sheet 1 I N, 160 2b 1w. 164

m 4 2 2 70 v HE /2 1 1 R /70 if 226 JOSEPH HEETE/CH Y I W fiwz I ATTORNEYS v June 18, 1946. J, HERTRICH TURBINE DRIVEN CENTRIFUGAL MACHINE V Filed June 18, 1941 5 Sheets-Sheet 2 INVENTOR 154 JOSEPH HEE'TE/CH I ATTORNEYS June 18, 1946. J. HERTRICH TURBINE DRIVEN CENTRIFUGAL MACHINE Filed Jfine 18, 1941 5 Sheets-Sheet 5 INVENTOR JOSEPH HEETE/CH Wm N R O June 18, 1946. J. HERTRICH TURBINE DRIVEN CENTRIFUGAL MACHINE 5 Sheets-Sheet 4 Fil-ed June 18, 1941 N9 V E V Hm n, r

, is 3 x a No Q P O0 0 L on J ORNEYS '226 '3 212 2 6 egh/jui I 210 I 2% Hi0 215 I 0 m 212 m j 5W 3 g E g 98 20299 INVENTOR June 18, 1946. J, HERTRICH 2,402,496

' TURBINE DRIVEN CENTRIFUGAL MACHINE I Filed Jun 18, 1941 5 Sheets-Sheet 5 JOSEPH HEPTE/CH h dxw ATTORNEYS TWRBINE DRIVEN CENTRHFUGAL Joseph Hertrich, Hamilton, one, assignor to The Western States chine (-ompany, lil'ialton, @hio, a. corporation oi Utah Application rum s, ran, serial No. teaser This invention relates to new and useful improvements in centrifugal machines, and particularly to suspended gyratory centrifugals provided with new combinations and new features ofconstruction which render the machines especially advantageous for use in the manufacture of sugar.

One of the objects oi my invention is to provide new and improved gyratory centrifugal apparatus for sugar manufacture and the like which is well suited ior operationsat very high speeds, say at 2000 to 2400 R. P. M. or higher when using 40" baskets, and which is preferable in many cases to the centrifugals heretofore used for such work, in both economy of construction and operating characteristics.

Another object of my invention is to provide centrifugal apparatus of that type having new features of flexibility or variability of operation such that the machines not only may be operated at very high speeds, 'or at any selected speed within the capacity of an installation, but also may be accelerated in each cycle at substantially constant rates which are variable within wide.

limits and hence can be pro-selected and controlled at will to satisfy best the processing requiremcnts of the particular sugar massecuite or other mixture undergoing treatment.

Another object is to provide such centrifugal apparatus which may be caused to accelerate at a predetermined substantiallyv constant rate during a part of each cycle and to shift automatically to a different rate of acceleration at a predetermined but variable interval after the start of the cycle.

Still another object of my invention is to provide improved turbine-driven centrifugal machines for sugar manufacture or the like which embody new combinations, new features of construction and new control systems that render the machines more cfilcient in operation and in other respects preferable to known turbine-driven centrifugal machines.

According to the present invention I provide centrifugal apparatus which is particularly useful for very high speed centrifugal operations, as in 21 Claims. (Cl. filth-72) 2 tion and hold the same at any desired rate within wide limits.

The impulse turbine which drives the machines is preferably a hydraulic or water motor of the Pelton wheel type. This includes a wheel secured to a vertical drive. shaft, a nozzle for directing a water jet against the wheel and a water housing surrounding the wheel to collect the escaping water, The centrifugal spindle and basket assembly may be of any suitable type that is sus-, pended from a gyratory centrifugal head for gyra tion or swinging movement; in response to unbalanced loads on'the assembly. The turbine drive shaft is mounted in fixed position between spaced vertical bearings, with its lower end disposed for connection with the upper. end of the centrifugal spindle through a flexible coupling in the centrifugal head. The turbine housing may provide support for these shaft bearings and may itself be mounted on conventional centrifugal I framework as normally located in sugar factories; and the centrifugal head may compriseand be suspended from the usual stationary hanger which in turn is supported from the same framework as the water housing, either directly or preferably through a direct connection with the base of the housing. In this way the water housing may be made of any desired size and capacity, and it becomes practical to use for high speed centrifugals a Pelton wheel of comparatively small diameter with a large how of water under moderately high pressure, instead oi employing a larger wheel with water under higher pressure as used with known water driven centrifugal machines. in addition, the wheel is kept stable at all times, so that it may operate at maximum efiiciency, and the center of gyration oi the centrifugal spindle may be located at the desired point for most emcient high speed operation without being limited by its association with the Water housing.

Control over the operating characteristics of the apparatus is effected through control and regulation of the turbine nozzle, which is provided blue power, and wherein there is an acceleration control system which controls the'rate of acceleration of the centrifugal and which may be changed in its setting was to vary the accelerawith a movable needle that governs the size of the jet opening and norinally is held in closed position by yieldable means such as a compression spring. The needle is movable away from closed position, to'allow a jet to be forced from the nozzle opening. against the buckets of the turbine wheel, when fluid pressure responsive means connected with the needle is actuated by the admission of fluid thereto under pressure. When the pressure fluid is cut oil, the nozzle may be closed by the action of the compression spring.

In association with this structure, the speed control system of the apparatus comprises a speed governor connected for rotation with the centrifugal, a normally closed needle valve or the like connected with the said pressure responsive means so as to relieve the pressure of fiuid theremember that is shifted from one position to another when the drive shaft and centrifugal have attained a predetermined speed of rotation. The actuating mechanism for the needle valve preferably is a servomotor linkage that is connected with both the valve needle and the movable needle of the turbine nozzle and arranged so that when the actuating member of the governor is shifted there will be a change in the position of this linkage, an opening of the valve to reduce the pressure of the pressure fluid and thereafter a continual action on the needle valve and the nozzle needle which will keep the centrifugal running smoothly at substantially the predetermined speed for which the governor has been set.

A characteristic of this speed control system is that the setting of the servomotor linkage determines or limits the extent of opening movement of the needle in response to fluid pressure while the machine is reaching its top speed. Control over the acceleration rate of the machine therefore may be obtained by varying the setting of the servomotor linkage, which will necessarily result in a corresponding variation in the size of the nozzle opening during acceleration and hence in the pressure or torque of the water jet on the Pelton wheel. This variation of the linkage setting may be obtained in a simple embodiment by providing the linkage with a connecting element of adjustable length, so that a change in the length of the connecting element will result in a change in the extent to which the nozzle needle is held open during acceleration.

In preferred embodiments of the invention, however, the apparatus is provided with additional control means for effecting predetermined or calibrated changes in the setting of the linkage. This control means may be disposed in a convenient location for manipulation by the centrifugal attendant whereby to select at will any desired rate of acceleration within a wide range for which the turbine may be designed. Furthermore, I have also provided automatic timing mechanism in association with the acceleration control system so that the centrifugal may be caused to accelerate at a predetermined 'rate during a part of each cycle and thereafter to change automatically to a different rate of acceleration, the time erations may be performed by operation of a single lever, either manually or automatically in response to suitable timing mechanism thatmay be provided to time and control automatically the stopping of the machine at the end of each cycle of operation. As indicated thereinafter, the timer to be employed for automatic variation of the accelerationrate of, the machine may be part of a timing mechanism common to the timer eminterval at which such change takes place and also the rate'of acceleration prior thereto being susceptible to adjustment at the will of thecentrifugal attendant. In embodiments such as these, changes in the setting of the servomotor linkage preferably are obtained by changing the position of one of the articulation points or pivots of the linkage.

The brake drum of the apparatus preferably is secured to the upper end of the turbine drive shaft, with the cooperating brake bands or shoes connected for activation by means of hydraulic cylinders or the like. Since the opening of the turbine nozzle to start and drive the machine and also the application of the brake to stop the machine take place in response to fluid or hydraulic pressure, the whole of the starting and stopping operations of the centrifugal may be ployed to stop the machine at'the end of each operating cycle.

The foregoing and other objects, features and advantages of my invention will become more apparent from the following description of an illustrative embodiment thereof, when considered in connection with the accompanying drawings. It is to be understood, however, that the new features and combinations which I have invented are defined particularly in the appended claims and that the same may be embodied in various forms and arrangements of apparatus without restriction to the illustrative embodiment. In the drawings,

Figure 1 is a front elevation showing an assembly of the illustrative embodiment with the centrifugal spindle and basket broken away.

Figure 2 is a plan view of the apparatus of Figure 1, showing the brake assembly and parts of the turbine control.

Figure 3 is a vertical section through the centrifugal and turbine assembly, along line 3--3 of Figure 2.

Figure 4 is an enlarged vertical section substantially along line 4-4 of Figure 2.

Figure 5 is a horizontal section substantially along line 5-5'of Figure 4, showing details of the governor construction.

Figure 6 is an enlarged horizontal section through the turbine nozzle and part of the water housing.

Figure 7 is a vertical section substantially along line l-I of Figure 6.

Figure 8 is a side elevation showing parts of the turbine nozzle and of the control linkage connected therewith.

Figure 9 is an end elevation of the structure shown in Figure 8. I

Figure 101s a front elevation showing the manually operable controls and the timing mechanism.

Figure 11 is a vertical section substantially along line lll l of Figure 10.

Figure 12 is a vertical section substantially along line l2--l2 of Figure 10.

Figure 13 is a section along line l3'l3 of Figure 11, showing detail construction.

Figure 14 is a vertical section substantially along line l4-i4 of Figure 11, and

Figure 15 is a plan view substantially along line l5--l5 of Figure 11.

Referring now to details of the illustrative embodiment, particularly to Figure 3, the assembly includes a suspended centrifugal spindle Ill carrying the usual perforate basket i2 at its lower end for rotation within a stationary casing or curb H. The spindle i0 is suspended from a gyratory head I6 of any suitable construction,

the illustrated head being similar to that dis-.

known form. Surrounding the wheel 2% is a water housing 26, the base of which rests upon conventional centrifugal framework B. In the illustrated embodiment; the hanger i8 is connected directly to the base of the housing 26, as at 28'.

Secured to the upper and lower parts of housing 26 are bearing supports 39 and 32, respectively. Bushings 3i and 33, respectively, within these supports embrace upper and lower parts of the drive shaft 22 and hold the shaft for rotation about a fixed vertical axis. To the upper end of shaft 22, above support til, there is keyed a brake adaptor 36 having an annular brake drum 38 secured thereto. The upper end of adaptor 36 has a flared hollow wall at 39 to provide a chamber accommodating a speed governor unit 52, hereinafter to be described.

The water housing 26 is provided with a nozzle M for directing a water jet against the buckets 25 of the Pelton wheel 26, and also with an outlet pipe 56 for discharging water from the housing. A. tube d8 vents air or vapors from the housing.

The turbine nozzle, as shown particularly in Figure 6, includes the nozzle body 5d having a replaceable, wear-resistant seat 52 therein to define the jet opening and having a tubular section 55 for the admission of water under pressure to drive the Pelton wheel. A needle 56 is carried by a reciprocable needle shaft 58 and is adapted normally to be held in a position closing the nozzle opening by means of a compression spring 68 which bears against the outer end of a plunger $2 secured to the needle shaft. This plunger, together with an inner end ring 5 thereof, serves as a piston which works in a cylinder 66 defined by the inner wall of a sleeve til secured to and constituting an extension of the nozzle body. A tube 70 (Figure 7) is provided to admit fluid under pressure into cylinder 65, and an outlet tube 72 is provided for relieving the pressure of such fluid under circumstances hereinafter described. Spring-loaded packings id and it, respectively, are provided on the plunger and at the inner end of the cylinder to seal the latter against the escape of the pressure medium admitted through tube iii. It will be apparent that when water, oil or other fluid under sufficient pressure is admitted to the cylinder 6%, the plunger will be caused to move outwardly against the resistance of the spring 6d, with the result of moving the needle shaft and moving needle 55 away from closed position to allow a water jet to pass through the nozzle opening and press against the buckets 25 of the Pelton wheel.

The brake mechanism of the apparatus (Figures 1 and 2) includes two oppositely disposed arcuate brake shoes 88, each having a suitable brake lining ti and being arranged to be forced into frictional engagement with the outer surface same box.

' turbine nozzle nor the brake is active.

ill)

of the brake drum 3t. Extending vertically from the upper end of the water housing 26 are two oppositely disposed stationary adaptor brackets 82 from which the brake mechanism is supported. These are joined together by a top plate 83 ex tending across and in spaced relation to the end of wall it (Figure 4). One end of each brake shoe is buckled to a bracket 82 through articulated links 84. The other end of each brake shoe is connected to the end of a brake plunger 35 having at its outer end a piston 88 reciprocable in a cylinder 90 that is swivelled to a part 92 integral with the corresponding adaptor bracket. A compression spring M in each brake cylinder normally urges the corresponding piston to a 6 position in which the brake shoe connected therewith is held out of engagement with the brake drum. Each cylinder, however, has a fluid con- .duit 98 opening'into its outer end, so that upon admission of fluid pressure into the cylinder through this conduit the piston Bil will be moved forwardly against the resistance of spring 9% and the brake linings therefor will be forced against the brake drum so as to retard rotation of the machine.

In the illustrated arrangement the fluid conduits 96 for the two brake cylinders stem from a common tube 91 that is connected with a valve 98 in a valve box 20% (Figures 1, i0, 11, i4 and 15). The inlet tube or conduit it for the needle cylinder 66 is connected with a valve it in the Each of the valves 98 and 95, as shown, is a three-way valve having a double valve seat 202 in which a stem 20% with corresponding seats operates. Each stem has a head 2% thereon and normally is held in its upper position by a spring 208. A valve shaft 2H2 extends across the heads 2% and carries eccentrics or cams its and 216 which are arranged in diiierent positions so as to engage and hold the respective heads and valve stems in their lower positions in certain settings of the shaft. Shaft 252 has 'a squared portion 285 in engagement with a leaf spring 256, so that the leaf spring will hold the shaft in any of at least three settings.

The box mil is secured by a bracket 2 it to the back of a control housing 22d, and an actuating shaft 222 extending through this housing is coupled to the valve shaft m, as by means of a flexible coupling 22d. A handle is provided on the front end of shaft 222 by which to move the latter to any of three positions. When the handle is moved to the position of Figure 10 it starts the machine; when moved to the extreme left it stops the machine; and its vertical position is a neutral position in which neither the This functional control is obtained as follows:

Hydraulic pressure is applied to the lower seat .of each of valves 98 and 99 from a water inlet are. With the valves'in neutral position, both valve stems 29s are held up by their springs 2%, and water flow is blocked off at the lower valve seats. When the handle 2% is turned to start position, the stem of valve as is lowered by cam 2M and the lower seat of this valve is opened while the upper seat is closed, valve 98 remaining unaffected. Water then flows into the body of seat 202, through a bore 22?, through a small gauge hole 228 inan adjustable throttle device 229i and thence into tube it and the nozzle cylinder $5. The gauge hole 228 limits the water flow to the nozzle cylinder in order that a speed con-' trol valve, hereinafter to be described, will work more efliciently. When handle 226 is turned back to neutral position the stem of valve 99 returns to its original position with its lower seat closed and its upper seat opened, so that water in the nozzle cylinder 65 then becomes free to flow back through the valve and to escape through a drain pipe 21!, thus allowing the nozzl needle 56to close under the influence of spring St.

A similar action takes place when handle'226 is turned to its stop position, except thatavalve 9% remains closed and valve E8 is opened so as to establish a pressure connection between a Water'inlet 2m and the tube 97! which transmits the pressure into the brake cylinders til. ,In thi condition of actuation, therefore, the brake is applied and the turbine nozzle is closed, which brings the machine to a stop or keeps it from rotation. When the handle is again moved away from the stop position, the water in the brake cylinders becomes free to flow back through valve 50 and pass off through the drain pipe 2I I, whereupon the brake shoes are released by the action of the springs 34.

As seen in Figures 3 and 4, the speed governor 42 is fixed to the top of the turbine drive shaft by means of a horizontal plate 43 which is bolted to the upper end flange of wall 40, as at 44, so as to permit removal of the governor as a unit. From plate 43 a cylindrical casing 45 extends downwardly into the chamber enclosed by wall '40, and carries at its lower end hubs I in which are journalled oppositely disposed horizontal shafts I02 for governor weights I04 that have an angled form substantially as shown in Figure 4. These weights include hubs I05 articulated on the shafts I02, vertically extended weight arms I08 and inwardly extended arms I01 having rounded ends I08 which bear against the lower face of a plug I09 at the lower end of .a nonrotary governor shaft or actuating member IIO. This shaft is supported in ball bearings III at the lower end of casing 45, and the outer races of these bearings are fitted into the lower end of a sleeve II2 which surrounds the governor shaft and is movable vertically therewith in casing 45. One or more compression springs II 4 and H5, confined within casing 45, bear'at one end against the lower end of sleeve H2 and at their upp r end against a nut I I8 which is adjustably threaded in the upper end of casing 45 and adapted vto be set in any position of adjustment by means of a set screw Ill. The governor chamber provided by wall 40 of the brake drum adaptor has a plate H8 in its bottom to form an oil seal, which allows the chamber to hold enough oil to keep the weight shafts I02 immersed in oil when the machine is not in rotation. When themachine rotates, this oil moves outward under centrifugal force and forms a wall against the inner face of the wall 40.

The upper portion of the governor shaft H0 is squared, as at I20, to slide vertically, but not to rotate, within an opening provided therefor in a stationary cap I22 in the top plate 83. It will be apparent that the compression springs II4 and H5 exert a certain downward pressure on the governor shaft which tends to hold the weight arms I08 in vertical position. When, however, the machine attains a definite speed of rotation the centrifugal force of the weight arms I06 becomes great enough to overcome the compression of these springs, whereupon the weight arms swing outwardly, as to dotted line position of Figure 4, and cause vertical movement of the governor shaft H0. The speed of rotation at which this shifting of the governor takes place may be varied by changing th governor springs I I4 and H5, or to a certain extent by changing the setting of the nut II6 so as to vary the compression of particular springs.

Secured to the top plate 83 in proximity to the governor 42 is a speed control or needle valve I30 having a valve seat I32, a valve needle I34 adapted to close a restricted opening through said seat, and chambers I38 and I38 on the lower and upper sides, respectively, of said seat. The needle I34 is carried by a reciprocable plunger I35, and a compression spring I31 normally holds the plunger downward with the needle in-clos'ed position. The outlet tube I2 from the nozzle cylinder. 88 extends to a point of connection with I34 is lifted from its seat there necessarily will.

be a release of pressure in cylinder 88 through tube I2 and the speed control valve, and when this occurs the compression spring of the turbine nozzle may move the needle 58 toward its closed position, thereby reducing the size of the water jet 'and, consequently, the torque of the turbine. Actuation of the speed control valve so as to effect such a reduction of pressure in the nozzle cylinder is accomplished as follows: A control rod I40 extends at one end into the valve plunger I35 and at its other end is articulated at I42 to the end of a lever arm I44. Between its ends rod I40 passes over a rounded end I45 of the governor shaft IIO. This rod constitutes an element of a servomotor linkage (Figures 1 and 4) which, besides arm I44, includes an arm I48 movable with the latter on a fixed shaft I41, a connecting rod I48 articulated at its upper end to the end of arm I46 and at its lower end to the end of a lever arm I48 that is movable around a pivot I50, and an arm I5I integral with arm I49 and connected with the outer end of the needle shaft 58 through a yoke I52 and pivots I58. The connecting rod I48 preferably is provided with adjustable threaded elements I54 by which to vary its length.

With this arrangement, assuming pivot I50 to be in a fixed position and the nozzle needle to be open with the machine accelerating, when the predetermined speed for which the governor has been set is reached by the machine, the governor shaft or actuating member IIO will rise, engage the control rod I40 at point D and thereupon move the plunger I35 and needle I34 of the speed control valve to a position allowing the escape of water from cylinder 68 through the restricted orifice of the needle valve seat I32. When this occurs, the spring 80 of the turbine nozzle will move the nozzle needle 58 toward closed position. Such movement of needle 58 and needle shaft 58, however, will necessarily move the servomotor linkage to a different position and thus raise the articulation point I42. The raising of point I42 thereupon allows the valve needle I34 to be moved to a certain extent toward closed position by means of spring I31. Consequently, any equilibrium condition becomes established which maintains the speed control valve needle I34 at a certain clearance, which in turn maintains a certain pressure condition in the nozzle cylinder 88 and therefore keeps the nozzle delivering the amount of power required to run the machine at its predetermined top speed.

It also will be evident that the setting of the servomotor linkage determines the extent to which the nozzle needle 58 may move away from closed position in response to pressure of fiuid in cylinder 85, and therefore that the setting of this linkage determines the size of the water Jet and the torque or acceleration characteristic of the turbine. This setting may be varied by adjusting elements I54 so as to change the length of the connecting rod I48. Thus it becomes possible to change the torque or accelerating characteristic of the centrifugal by changing the length of the connecting rod, for that controls the nozzle opening during the period when the aeoasee governor is not active d thereby controls the pressure of the water Jet against the Pelton wheel.

ting of the acceleration control system and placing it under convenient manual or automatic control. For example, the pivot wt for the lever arms M9 and iEi of the servomotorlinkage is carried by arm ltd of a lever fulcrumed on a fixed pivot 162. Another arm we of the same lever is pivotally connected with the upper end of a rod I66 and normally is urged in a clockwise irection with respect to pivot I82, as by means of a spring E58. The lower end of rod B6B (see Figures 10 and 12) is articulated to an arm 669 keyed to a shaft I it. In spaced relation to arm I69 and fixed to the same shaft is a do H2 which is arranged to bear at its end against the periphery of a rotary cam H t. Cam lid is mounted on a shaft lit extending across the housing 228, and at the forward end of shaft I16 there is a dial H8 which may be turned so as to turn cam lid, change the elevation of the end of dog H2, and thereby change the position of the pivot l5 constituting part of the servomotor linkage. Such changes obviously result in corresponding changes in the setting of the linkage and in the maximum extent to which the nozzle needle may move away from closed position in response to hydraulic pressure in cylinder 66.

The periphery of the cam lldextends spirally from a low point to a high point where there is a radial drop back to the low point, as seen in broken lines in Figure 10. The dial lift is marked with graduations which correspond to different elevations of the cam and therefore to different acceleration rates of the machine. A wing screw We may be set to hold the cam shaft lit and cam lid in any desired position of angular adjustment.

In addition, it may be desired under certain circumstances to provide for a quick change in the accelerating power of the turbine without changing the setting of the dial W8, as when it is desired to accelerate the centrifugal at a predetermined slow rate during the first part of a cycle and to change its acceleration to the maximum rate within the turbine power before the machine reaches its top speed. This may be accomplished manually as follows: Cam lid is mounted on shaft H6 through a sleeve use against which bears a compression spring i8 1, so as normally to hold the c m beneath the end of dog H2. The cam and cam shaft, however, are free to slide axially against the resistance of spring i8 3, there being a splined connection at m5 with a bushing Hill which carries the dial W3. A yoke ltd, mounted freely on shaft l'lfi, embraces a groove H59 in sleeve 582 (Figure 12), so that forward movement of this yoke results in an axial shifting of cam Ht away from its normal position beneath the dog 872. Such movement of the yoke may be effectuated at will by forward movement of a handle I953 loosely carried on shaft i'lll. which handle acts through a detent I92 to swing the yoke. When this occurs, the spring I68 acting on the lever arm 66d causes the dog H2 to drop and causes the nozzle needle 56 to move to its maximum open position. To restore the cam lid to a position beneath the dog E12, the handle I9!) is provided with a detent Ht that engages and liftsdog llfi'on the backward stroke of the handle, thereby allowing spring I86 to return the cam to its original position.

In order to cool the brake drum 38 so as to prevent overheating thereof and excessive wearing of the brake liningsBl, the brake is provided with a suitable water cooling system, for example of the type disclosed and claimed in United States Letters Patent No. 2,096,341. An inlet pipe 230 (Figure -1) is provided to convey cooling water into the drum.38, where it forms an annular wall against the inside of the drum during rotation of the machine. .Pipe 230 leads from a springning the'water within the drum falls and iamtained in the receptacle formed by the drum 38 and the brake adaptor 36. Excessive water is drawn off during operation of the machine through a discharge pipe 23d, as shown in said Patent No. 2,096,341.- The valve 232 is adapted to be opened when the machine starts in operation and to be closed at the end of each operating cycle in order to keep water from overflowing the receptacle inside of drum 38. This operation may be obtained, for example, by means of a detent 236 on a lever 240 which is connected with the actuating handle 225 through a link 238. As seen in Figure 1, movement of handle 226 to the right, or the starting position, will result in the opening of valve 232, and when lever 22s rests in its neutral or stop position the cooling water valve is kept closed by its spring.

The foregoing description of the illustrated embodiment will indicate the construction and manner of operation of this embodiment when operated entirely under manual control. Assuming that the apparatus is being used for the purging of sugar massecuite or the like, the attendant may set the dial H8 at a graduation correspond ing to the acceleration rate desired at the start of the cycle and may then load the basket 12 with a charge of the mixture undergoing treatment. After the loading operation, the attendant simply turns handle 226 to the starting position, whereupon water under pressure passes into the nozzle cylinder $6 from valve 99 and the machine starts accelerating at the predetermined rate, with the brake in off position. If desired, the

machine may be allowed to accelerate to top speed v shaft H0 moves so as to shift the servomotor linkage, which opens the speed control valve I30 and establishes an equilibrium condition holding the machine at its predetermined speed. When the desired period of operation has expired, the attendant may move the handle 226 to its extreme left position. whereupon the turbine nozzle is closed by spring 60 and water pressure is applied to the brake cylinders through valve 98 to stop the machine.

In addition to these provisions for manual control of the operations. however, the control .system is provided with an automatic timing mechanism 250 which functions at the end of a predetermined but variable period to stop the madescribed.

chine automatically and also, if desired, to shift the acceleration control at a. predetermined but variable interval after the start of each cycle.

This timing mechanism is mounted adjacent to housing 220, and its casing 252 may provide support for the cooling water valve 232 hereinabove In construction and operation the 11 Eugene Roberts. Extending within the housing 252 is a timer shaft 254 which carries a timer head 256 at its outer end. A saw-tooth clutch (not shown) within housing 252, and suitable gears 258, are adapted to connect the timer shaft 254 for rotation with a parallel drive shaft 266 that revolves at a constant speed. The lever 246 connected with handle 2.26 operates to engage the timer clutch when handle 226 is moved to starting position, thereby causing a slow counterclockwise movement of the timer head 256 away from its initial or zero position. A torsion spring 262 connected with the timer shaft functions to return the head to its initial position when the clutch within housing 252 .is disengaged, which occurs whenever handle 226 is moved away from the starting or running position.

The timer head 256 includes a plurality of adjustably related timer discs, such as 264 and 266. These discs may be set in any desired relative position by pulling and manipulating knobs 268 on the face of the timer head, as disclosed in said Patent No. 1,956,539 The discs 264 and 266 carry radial fingers 265 and 261, respectively, which act to shift the acceleration control and to cause a shifting of the control shaft 222 at predetermined but variable intervals after the start of each cycle.

Finger 261 acts on the acceleration control system by engaging a detent 280 carried on a radial arm 28| that is connected with a sleeve 262 from which the yoke I88 is supported. It will be evident that when finger 261 contacts'and moves detent 280, a clockwise movement of arm 26! and yoke I88 occur so as to shift the cam I14 from beneath the end of dog I12. This of course establishes the maximum opening of the nozzle needle and causes the machine to accelerate at full power. The time when this occurs is varied by varying the initial setting of disc 266 and finger 261.

Finger 265 acts to stop the machine automatically in the following manner: The control shaft 222 has a disc 290 loosely mounted thereon which is urged in a clockwise direction, as viewed in Figure 10, by means of a torsion spring 292. A pin 294 integral with disc 290 extends parallel to shaft 222, and a radial arm 296 keyed to said shaft is adapted to engage and to be engaged by said pin. The disc 290 has a radial shoulder 296 which is formed to abut against the end of a lever arm 300. Another arm 302 of the same lever extends upwardly to a point where a transverse end 304 thereof will lie in the path of tumlng movement of finger 265. Therefore, when handle 226 is turned to the right to start the machine, arm 296 engages pin 294 on disc 290 and moves the disc until the end of arm 300 engages behind the disc shoulder. When a predetermined period of time, as determined by the initial setting of finger 265, has expired, this finger engages the end 304 of arm 302 and lifts this arm so as to free the end of arm 300 from the disc shoulder. Thereupon the torsion spring 292 turns the disc in clockwise direction, causing pin 29! to abut against arm 296 and turn the control shaft and handle 226 to their stop position. This, as previously described, cuts off hydraulic pressure to the nozzle cylinder and establishes pressure in the brake cylinders so as to stop the machine.

It will be understood that the control mechanisms shown in Figure or other equivalent mechanisms may be mounted in any desired position for convenient manipulation by an attendant of the centrifugal. While I have Shown them as being supported from the framework B, this has been done merely for convenience of 11- lustration. Also, the timing control mechanisms may be provided with additional timers and motivating systems to be actuated thereby for controlling the operation of sprayers and syrup separators in centrifugals provided with such devices,

the .art.

It also will be understood, as hereinbefore mentioned, that each of the several new features and combinations of my invention, either alone or in combination with other new features here disclosed, may be embodied in various different fonns of apparatus without restriction to the illustrated embodiment. Itherefore desire that my invention be accorded a scope fully commensurate with its contributions to the art, as intended to be set forth in the appended claims,

I claim:

1. In a centrifugal machine comprising a stationary hanger supporting a suspension head and a gyratory basket-carrying spindle suspended from said head, the combination therewith of an impulse turbine above said hanger comprising a, vertical drive shaft, an impulse wheel secured to said shaft intermediate its ends, a nozzle for directing a fluid jet against said wheel, said nozzle having a movable needle to govern the size of said jet, and a stationary housing for fluid surrounding said wheel, a flexible coupling connecting the lower end of said shaft for rotation with said spindle, said shaft extending above said housing and having a hollow extension upon its upper end, a speed governor secured to and located within said extension, and means movable by said governor and operating upon said needle for controlling the position of said needle.

2. In a suspended, gyratory centrifugal having a basket-carrying spindle and a hydraulic turbine connected with said spindle for driving the centrifugal, the combination of a vertical turbine shaft mounted in fixed bearings above said spindle, a flexible coupling connecting said shaft with said spindle, an impulse wheel secured to said shaft, a stationary water housing surrounding said wheel intermediate the ends of said shaft, a nozzle for directing a water jet against said wheel and having an adjustable needle therein for controlling the size of the jet, a speed governor secured for rotation with said shaft, and needle control means repsonsive to said governor for causing movement of said needle to reduce the size of said jet when the centrifugal has reached a predetermined speed.

.3. In centrifugal apparatus comprising a suspended gyratory spindle and a centrifugal basket carried at the lower end of said spindle, the combination therewith of a hydraulic turbine including a fixedly mounted turbine shaft located above and connected for rotation with said spindle, an impulse wheel secured to said shaft, a nozzle for directing a water jet against said wheel, said nozzle having an adjustable needle therein for varying the -nozzle opening, a stationary water housing surrounding said shaft for collecting water discharged from said wheel, aspeed governor connected for rotation with said shaft, and a servomotor linkage connected with said needle and associated with said governor for movement thereby so as to move said needle toward closed position when the centrifugal approaches a predetermined speed.

4. In a machine comprising a rotary driven shaft and a hydraulic turbine connected to drive eaoacee 13 the same including an impulse wheel, a water housing surrounding said wheel and a nozzle for directing a water jet against said wheel, a nozzle needle carried by a movable needle shaft within said nozzle for varying the nozzle opening, spring means acting on said shaft to urge said needle to closed position, a cylinder having a piston therein secured to said shaft and adapted to be actuated by fluid under pressure to move said needle away from closed position against the resistance of said spring means, fluid inlet and outlet tubes connected with Said cylinder, a valve for admitting fluid under pressure to said inlet tube, and control means including a needle valve remote from said nozzle and connected with said outlet tube for reducing the pressure of fluid in said cylinder to control the speed of said turbine, said needle valve having a spring normally urging the same to closed position, a speed governor connected for rotation with said driven shaft, a shiftable. element moved by said governor to a predetermined position in response to a predetermined high speed of said driven shaft, and linkage connected with said needle valve and positioned to be engaged and moved by said element, when the latter is moved to said predetermined position, for opening said needle valve against the resistance of said spring.

5. In a machine comprising a rotary driven shaft and a hydraulic turbine connected to drive the same including a vertical driving shaft having an impulse wheel secured thereto, a water housing surrounding said wheel and a nozzle for directing a water Jet against said wheel, a movable nozzle needle for varying the nozzle opening, spring means urging said needle to closed position, fluid pressure responsive means for overbalancing the force of said spring means and moving said needle away from closed position, a control system for admitting or restraininga supply of fluid under pressure to or from said pressure responsive means, and a speed control system operative automatically when the driving shaft has attained a predetermined speed for regulating the position of said needle, said speed control system including a normally closed control valve for relieving fluid pressure on said pressure responsive means, a speed governor connected for rotation with said driving shaft, a

shiftable element movable by' said governor to a predetermined position in response to a predetermined high speed of rotation of said driving shaft, a servomotor linkage connected with said control valve and positioned to be engaged and moved by said element, when the driving shaft has attained said predetermined speed, so as to open said control valve and cause closing movement of said needle under the force of said spring means, said linkage having connections with said needle so that closing movement of said needle displaces said linkage with respect to said element and moves said control valve to maintain substantially said predetermined speed.

6. In a machine comprising a rotary driven haft and a hydraulic turbine connected to drive the same including a driving shaft mounted in fixed bearings and having an impulse wheel secured thereto, a water housing surrounding said wheel and a nozzle for directing a water jet against said wheel, a movable nozzle needle governing the size of the nozzle opening, yieldable mean normally holding said needle in closed position, fluid pressure responsive means for overbalancing the force of said yieldable means and moving said needle away from closed position, a

normally closed control valve for relieving fluid pressure on'said pressure responsive means, a servomotor linkage connected with said needle to limit the opening movement thereof and to be moved by closing movement thereof, said linkage including a member also connected with said control valve and operable to move the same, a speed governor connected for rotation with said driving shaft, a shiftable element moved by said governor, when the driving shaft has attained a predetermined speed, a predetermined position where said element engages and moves to said linkage member so as to open said control valve. said linkage being operative thereafter in response to movements of said needle and said element to vary the positions of said control valve and needle so as to keep the driving shaft rotating substantially at said predetermined speed, and adjustable means for varying the setting of said linkage so as to vary the extent of opening movement of said needle and thereby control the accelerating rate of the shafts.

'7. In a suspended gyratory centrifugal machine having an impulse turbine connected therewith to drive the same, said turbine having a driving linkage connected with said nozzl and rendered operative by said governor when the machine has attained a predetermined speed for reducing the nozzle opening so as to keep the machine running at substantially said predetermined speed, and acceleration control means connected with said linkage and having manually operable means to adjust the setting thereof for predetermining and controlling the size of the nozzle opening before the machine has attained such speed whereby to control the rate of acceleration of the machine.

8. In a suspended gyratory centrifugal having an impulse turbine connected therewith for driving the same, said turbine including a nozzle haviing a needle movable to vary the nozzle opening, the combination therewith of starting control means connected with the turbine nozzle and arra ged to be actuated manually by an attendant,

rotary timer to be started in rotation upon actution of said starting control means as aforesaid, and means connected with said linkage and shiftable by said timer element after a predetermined period of its rotation for automatically changing the setting of said acceleration control means during the acceleration of the centrifugal.

9. In a suspended gyratory centrifugal having an impulse turbine connected therewith for driving the same, said turbine including a nozzle havsure system connected with the nozzle including a control valve adapted when opened to admit fluid under pressure to said pressure responsive means,

manually operable starting mean for opening said valve, automatically operable timing mechanism adapted to be started upon the operation of said starting means and including at least two timers capable of independently adjustable time settings, means rendered active by one of said timers for closing said valve at the end of a predetermined but variable period after the operation of said starting means, adjustable acceleration control means connected with said needle for governing the nozzle opening during the acceleration of the centrifugal, and means connected with said acceleration control means and actuated by another of said timers for automatically changing the setting of said acceleration control means at the end of a predetermined but variable period after the operation of said starting means.

10. In a suspended gyratory centrifugal having an impulse turbine connected therewith for driving th same, said turbine including a nozzle having a needle movable away from closed position to vary the nozzle opening, the combination of means to impose a yielding resistance against such needle movement, fluid pressure responsive means for so moving the needle, a starting valve adapted when opened to admit fluid under pressure to said pressure responsive means, a control valve adapted when opened to reduce the pressure of such fluid on said pressure responsive means. manually operable control means for opening and closing said starting valve, an automatic speed control system including a speed governor connected for rotation with the centrifugal and a servomotor linkage connected respectively with said needle and said'control valve and associated with said governor for actuation thereby so as to open said control valve when the centrifugal has attained a predetermined speed, and adjustable means connected with said linkage for governing the size of the nozzle opening from the opening of said starting valve until the opening oi said speed control valve, whereby to govern the rate of acceleration of the centrifugal.

11. In a suspended gyratory centrifugal having an impulse turbine connected therewith for driving the same, said turbine including a nozzle having a needle movable away from closed position to vary the nozzle opening, the combination of means to impose yielding resistance against such movement, fluid pressure responsive means for so moving the needle, a starting valve adapted when opened to admit fluid under pressure to said pressure responsive means, a control valve adapted when opened to reduce the pressure of such fluid on said pressure responsive means, manually operable control means for opening and closing said starting valve, an automatic speed control system including a speed governor connected for rotation with the centrifugal and a servomotor linkage connected respectively with said needle and said control valve and associated with said governor for actuation thereby so as to open said control valve when the centrifugal has attained a predetermined speed, a variable acceleration control system connected with said" linkage for controlling; the setting of said linkage so as to govern the size of the nozzle opening during acceleration of the centrifugal, timing mechanism arranged to be started in operation in definitely timed relation to the opening of said starting valve and including at least two timers each capable of variable time settings, means associated with said control means and one of said timers for actuation by the latter so as to close said starting valve at the end of a predetermined but variable period after the opening thereof, and means associated with said acceleration control system and another of said'timers for actuation by such other timer for changing the setting of said linkage so a to change the size of the nozzle opening at the end of a predetermined but variable period after the opening of said starting valve.

12. A combination as described in claim 11, and a manually operable member connected with said acceleration control system for varying the setting of the latter at will.

13. In a machine comprising a rotary driven shaft and a water turbine for driving the same including a vertical drive shaft mounted in fixed bearings and connected for rotation with said driven shaft, an impulse wheel secured to said drive shaft, a water housing surrounding said wheel and a nozzle for directing a water jet against said wheel. said nozzle having a needle therein movable away from closed position to form the jet opening, fluid pressure responsive means for so moving the needle and means yieldably to urge the needle toward closed position, a speed governor mounted on the upper end of said drive shaft, a non-rotary shiftable element moved by said governor to a predetermined position when said shaft has attained a predetermined full speed, a spring-closed needle valve disposed adjacent to said shiftable element and connected with said fluid pressure responsive means so as, when opened, to reduce the pressure of fluid on the latter, and a servomotor linkage mounted for movement relative to two fixed pivots and connected with said nozzle needle beyond one of said pivots so as to limit the size of the let opening, said linkage being connected beyond the other of said pivots with said needle valve through an articulated rod disposed in the path of movement of said shiftable element so that said linkage is 40 moved by said element to open said valve when said element is moved to said predetermined position.

14. In a machine comprising a rotary driven shaft and a water turbine for driving the same including a vertical drive shaft mounted in fixed bearings and connected for rotation with said driven shaft, an impulse wheel secured to said drive shaft, a water housing surrounding said wheel and a nozzle for directing a water jet against said wheel, said nozzle having a needle therein movable away from closed position to form the jet opening means to impose yieldable resistance against such needle movement and fluid pressure responsive means for so moving the'needie, a speed governor mounted on the upper end of said drive shaft, a non-rotary shiftable element moved by said governor to a predetermined position when said shaft has attained a predetermined full speed, a spring-closed needle valve disposed adjacent to said shiftable element and adapted when opened to reduce the pressure of fluid on said fluid pressure responsive means, and a servomotor linkage mounted for movement relative to two fixed pivots and connected with said nozzle needle beyond one of .said pivots so as to limit the size of the jet opening, said linkage being connected beyond the other of said Pivots with said needle valve through an-articulated rod disposed in the 7 path of movement of said shiftable element so that said linkage is moved by said element to open said valve when said element is moved to 11 of the linkage and thereby the acceleration rate of the machine.

15. In a machine comprising a rotary driven shaft and a water turbine for driving the same including a drive shaft mounted in fixed bearopening means to impose yieldable. resistance against such needle movement, and fluid pressure responsive means for so moving the needle, a speed governor mounted on an end of said drive shaft, a non-rotary shiftable element movedby said governor to a predetermined position when said shaft has attained a predetermined full speed, a spring-closed needle valve disposed adjacent to said shiitable element and adapted when opened to reduce the pressure of fluid on said fluid pressure responsive means, a servomotor linkage mounted for movement relative to two fixed pivots and connected with said nozzle needle beyond one of said pivots so as to limit the size of the jet opening, said linkage being connected beyond the other of said pivots withsaid needle valve through an articulated rod disposed in the path of movement of said shiftable element so that said linkage is moved by said element to open said valve when said element is moved to said predetermined position, and acceleration control means capable of being set in various positions at the will of an attendant for varying the position of one of said pivots and thereby varying the setting of said linkage and the acceleration rate of the machine. 1

16. In a machine having an impulse turbine for driving the same, including a water nozzle for the turbine wheel having a needle movable to open position to start, the machine, a movable linkage connected with said needle to govern the extent of its opening movement, and 'a variable controller connected with said linkage to establish the setting thereof, said controller comprising a dog connected with said linkage, a movable cam to determine the position of said dog, and a manually operable member to vary the setting of said cam.

17. In a machine having an impulse turbine for driving the same, including a water nozzle for the turbine wheel having a needle movable to. open position to start the machine, a movable linkage connected with said needle to govern the extent oi its opening movement, and a variable controlier connected with 'said linka to establish the setting thereof, said controller comprising a pivotally mounted dog connected with said linkage, a rotatable cam normally limiting movement of said dog, means urging said dog against said cam, manually operable means for turning said cam to vary the setting of said dog, and means for shifting said cam axially to free said dog from said cam.

18. In a machine having an impulse turbine for driving the same, including a water nozzle for the were cam, manually operable mean for turning said cum to vary the setting of said dog, and means for shifting said cam axially to free said dog from said cam, said-last-recited means including a rotary timer having an adjustable arc of rotation and a device operated by said timer so as to shift said cam after a predetermined but variable period of rotation of said timer.

19. In a machine having an impulse turbine for driving the same, including a water nozzle for the turbine wheelhaving a needle movable to open connected with said needle to govern the extent position to start the machine, a movable linkage of its opening movement, and a variable controller nn d with said linkage to establish the setting thereof, said controller comprising a pivotally mounted dog connected with said linkage, a rotatable I camnormally limiting movement of said dog, means for urging said dog against said cam, manually operable means for-turning said cam to vary the setting of said dog, a spring normally holding said cam in alignment with said dog, a hand lever having means thereon-for shifting said cam axially against said spring so as to free said dog when the lever is moved in one direcimpulse wheel fixed to said shaft intermediate said bearings, a fiexible'coupling connecting the lower end of said shaft with the upper end of said spindle in said head, a hollow brake adaptor carrying a vertical brak drum and secured directly to the upper end of said shaft, said adaptor having a hollow axial extension open at the top and disposed at least partly within the confines of said drum, a stationary water housing surrounding said shaft and said wheel between said adaptor and said head. a water nozzle mounted on said housing for directing a water jet against said wheel, said nozzle having a movable needle to govern the size of said jet, and means including a speed governor unit secured to and located inside said extension and connections movable by said governor and operating upon said needle for controlling the position of said needle.

, 21. In a suspended gyratory centrifugal having an impulse turbine connected therewith for driving the same, the combination of a turbine nozzle having a needle movable away from closed position to establish the nozzle opening, fluid pressure responsive means for so moving the needle, a system for applying fluid pressure to said pressure responsive means, said system including j a control valve adapted when opened to admit fluid under pressure to said pressure responsive means, manually operable starting means for opening said valve, timing mechanism including a timer adjustable to various time settings, man- JOSEBH ilf :i- TRICK.

Certificate of Correction Patent No. 2,402,496. June 18, 1946i JOSEPH HERTRIOH It is hereby certified that errors appear in the printed specification of the above numbered patent requiring correction as follows: Column 4, line 6, for thereinafter read hereinafter; column 8, line 53, for any readan; column 14, line 12, claim 6,

' strike out to and insert the same in line 11, same claim, after the word and comma speed,; and that the said Letters Patent should be, read with these corrections therein that the same may conform to the record of the case 1n the Patent Oflice. Y

'Signed and sealed this 3rd day of September, A. D. 1946.

LESLIE FRAZER,

First Assistant Oommiaaioner cf Patents. 

